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CN103527732B - A kind of seven gear planetary automatic transmissions - Google Patents

A kind of seven gear planetary automatic transmissions Download PDF

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Publication number
CN103527732B
CN103527732B CN201310487758.8A CN201310487758A CN103527732B CN 103527732 B CN103527732 B CN 103527732B CN 201310487758 A CN201310487758 A CN 201310487758A CN 103527732 B CN103527732 B CN 103527732B
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CN
China
Prior art keywords
driving member
planet row
brake
clutch
gear
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Active
Application number
CN201310487758.8A
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Chinese (zh)
Other versions
CN103527732A (en
Inventor
王明成
冯光军
石彦辉
姜宏暄
李慎龙
贾爽
李吉元
王景霞
徐飞
望运虎
王颖楠
李翠芬
韩宇石
李志伟
衣超
于定跃
潜波
刘越
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
North Tomson Transmission Technology Co.,Ltd.
Original Assignee
China North Vehicle Research Institute
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Publication date
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Priority to CN201310487758.8A priority Critical patent/CN103527732B/en
Publication of CN103527732A publication Critical patent/CN103527732A/en
Application granted granted Critical
Publication of CN103527732B publication Critical patent/CN103527732B/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H2003/445—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the input and the set of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0056—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The invention belongs to system of vehicle transmission technical field, and in particular to a kind of seven gear planetary automatic transmission.For making two drive shifts for overgear, gear range be big, performance is more excellent, meet the use requirement of wheeled vehicle, seven gear planetary automatic transmissions that the present invention is provided, including planet row, the input link being connected with input shaft, output shaft installed in two ends respectively, output link, driving member, brake and clutch, the planet row has three, the driving member has four, and the brake has four, and the clutch has two.Thus, seven gear planetary automatic transmission achieves seven drive shifts, and gear range can reach 8.941；Three planet rows are the simple planet row of single star, and k value is in the range of 1.7～2.6, compact conformation, reduces the volume and weight of speed changer.

Description

A kind of seven gear planetary automatic transmissions
Technical field
The invention belongs to system of vehicle transmission technical field, and in particular to road vehicle is with a kind of seven gear planetary automatic transmission.
Background technology
Used as road vehicle automatic transmission, the power such as internal combustion engine reaches planetary automatic transmission through fluid torque-converter Input shaft, after current gear speed change, power is exported from output shaft, and reaches left and right driving wheel through differential mechanism, and speed changer Great majority are made up of multiple planet rows, brake and clutch.At present, the road vehicle of main flow is with seven grades of planetary automatic speed-changings Device gear range is larger, and is four planet rows, and volume and weight is larger.For this purpose, it is little to find a kind of gear range, fit Seven gear planetary automatic transmissions of road vehicle are closed, using three planet row schemes, to reduce volume and weight.
Content of the invention
(1) technical problem to be solved
It is an object of the invention to provide a kind of seven gear planetary automatic transmissions of vehicle, the automatic transmission is using three Planet row, two clutches and four brakes realize seven drive shifts and a reverse gear, and two drive shifts therein are hypervelocity Shelves, gear range are moderate, and volume and weight is little, and performance is more excellent, can meet road vehicle to close steps scope, lightweight The demand of seven gear planetary automatic transmissions.
(2) technical scheme
For solving above-mentioned technical problem, seven gear planetary automatic transmission of one kind that the present invention is provided, including planet row, install The input link 1 that is connected with input shaft, output shaft at two ends respectively, output link 2, driving member, brake and clutch, institute Stating planet row has three, respectively planet row PGS1, planet row PGS2 and planet row PGS3；The driving member has four, point Wei not driving member 3, driving member 4, driving member 5 and driving member 6；The brake has four, respectively brake B1, Brake B2, brake B3 and brake B4；The clutch has two, respectively clutch C1 and clutch C2；
The planet row PGS1 is connected with input link 1, driving member 4 and driving member 3 respectively；
The planet row PGS2 is connected with driving member 4, driving member 5 and output link 2 respectively；
The planet row PGS3 is connected with driving member 6, output link 2 and driving member 5 respectively；
The sun gear S1 respectively with planet row PGS1 of the input link 1, the interior hub of clutch C1 and clutch C2's is outer Hub connects；
The output link 2 is connected with the planet carrier CA3 of the gear ring R2 and planet row PGS3 of planet row PGS2 respectively；
The driving member 3 is connected with the interior hub of the gear ring R1 and brake B1 of planet row PGS1 respectively；
The driving member 4 planet carrier CA1, the sun gear S2 of planet row PGS2 respectively with planet row PGS1 and brake The interior hub connection of B2；
The planet carrier CA2 respectively with planet row PGS2 of the driving member 5, the gear ring R3 of planet row PGS3, clutch C2 Interior hub and brake B3 interior hub connection；
In the sun gear S3 respectively with planet row PGS3 of the driving member 6, the outer hub and brake B4 of clutch C1 Hub connects；
The brake B1 is used for brake component 3；
The brake B2 is used for brake component 4；
The brake B3 is used for brake component 5；
The brake B4 is used for brake component 6；
The clutch C1 connection input link 1 and driving member 6；
The clutch C2 connection input link 1 and driving member 5；
Wherein, the planet row is the simple planet row of single star.
Wherein, each described planet row includes sun gear, planet carrier and gear ring respectively.
(3) beneficial effect
Compared with prior art, the present invention possesses following beneficial effect：
Seven gear planetary automatic transmissions that the present invention is provided are using three planet rows, four brakes and two clutches Scheme, it is achieved that seven drive shifts, gear range can reach 8.941；Three planet rows are the simple planet row of single star, and k It is worth in the range of 1.7～2.6, compact conformation, reduces the volume and weight of speed changer.
Description of the drawings
The each part annexation schematic diagram of seven gear planetary automatic transmissions that Fig. 1 is provided for the present invention, in figure PGS1～ PGS3 is three planet rows, and S1～S3 is three sun gears, and CA1～CA3 is three planet carriers, and R1～R3 is three gear rings, B1 ～B4 is four brakes, and C1～C2 is two clutches, and 1 is input link, and 2 is output link, and 3～6 is driving member.
Specific embodiment
For making the purpose of the present invention, content and advantage clearer, with reference to the accompanying drawings and examples, the tool to the present invention Body embodiment is described in further detail.
Seven gear planetary automatic transmissions that the present invention is provided are applied to road vehicle.Wherein each planet row is arranged in order, Connected using driving member between each planet row, input shaft is connected with input link 1, generally the turbine of fluid torque-converter Axle, for reaching speed changer by the power of engine through fluid torque-converter.Output shaft is connected with output link 2, by transfer gear Or power is reached forward and backward bridge or left and right driving wheel by differential mechanism.The planetary automatic transmission is completely right with respect to pivot Claim, the latter half of pivot is eliminated in Fig. 1, is no longer explained when below describing.
As shown in figure 1, seven gear planetary automatic transmissions, including planet row, installed in two ends respectively with input shaft, output shaft The input link 1 of connection, output link 2, driving member, brake and clutch, the planet row have three, respectively planet Row PGS1, planet row PGS2 and planet row PGS3；The driving member has four, respectively driving member 3, driving member 4, biography Dynamic component 5 and driving member 6；The brake has four, respectively brake B1, brake B2, brake B3 and brake B4；The clutch has two, respectively clutch C1 and clutch C2；
Each described planet row includes sun gear, planet carrier and gear ring respectively.
The planet row PGS1 includes sun gear S1, planet carrier CA1 and tri- revolving parts of gear ring R1, respectively with input link 1st, driving member 4 and driving member 3 connect, and sun gear S1 is connected with input link 1 with input power, can pass through brake B1 system Dynamic gear ring R1 is so that the rotating speed of input link 1 is carried out deceleration output as middle output by planet carrier CA1.
The planet row PGS2 includes sun gear S2, planet carrier CA2 and tri- revolving parts of gear ring R2, respectively with driving member 4th, driving member 5 and output link 2 connect, and can brake planet carrier CA2 so that gear ring R2 is used as in reduction gear by brake B3 The rotating speed of sun gear S2 is carried out deceleration output by middle output, or sun gear S2 is braked by brake B2 in speedup shelves so that The rotating speed of planet carrier CA2 is carried out speedup output as middle output by gear ring R2.
The planet row PGS3 includes sun gear S3, planet carrier CA3 and tri- revolving parts of gear ring R3, respectively with driving member 6th, output link 2 and driving member 5 connect, and can brake gear ring R3 by brake B3 so that planet carrier CA3 is used as output general The rotating speed of sun gear S3 carries out deceleration output.
The sun gear S1 respectively with planet row PGS1 of the input link 1, the interior hub of clutch C1 and clutch C2's is outer Hub connects；
The output link 2 is connected with the planet carrier CA3 of the gear ring R2 and planet row PGS3 of planet row PGS2 respectively；
The driving member 3 is connected with the interior hub of the gear ring R1 and brake B1 of planet row PGS1 respectively；
The driving member 4 planet carrier CA1, the sun gear S2 of planet row PGS2 respectively with planet row PGS1 and brake The interior hub connection of B2；
The planet carrier CA2 respectively with planet row PGS2 of the driving member 5, the gear ring R3 of planet row PGS3, clutch C2 Interior hub and brake B3 interior hub connection；
In the sun gear S3 respectively with planet row PGS3 of the driving member 6, the outer hub and brake B4 of clutch C1 Hub connects；
The brake B1 is used for brake component 3；
The brake B2 is used for brake component 4；
The brake B3 is used for brake component 5；
The brake B4 is used for brake component 6；
The clutch C1 connection input link 1 and driving member 6；
The clutch C2 connection input link 1 and driving member 5；
The planet row is the simple planet row of single star.
Brake B1～B4, clutch C1 and C2 are generally multiple-piece friction manipulation part, drive piston to enter using hydraulic oil Row pressurization.The manipulation schemes of each shelves are realized as shown in table 1.
1 seven gear planetary automatic transmission implementation of table and corresponding gearratio, a ratio illustrate table
In table, "○" represents that controls is combined
The example of the present invention is described in detail with reference to Fig. 1 and Biao 1, it should be noted that, transmission described herein Than referring to the ratio of input shaft rotating speed and output rotating speed, planet row k value refer to the gear ring number of teeth of planet row and the sun gear number of teeth it Than.
When brake B1 and brake B4 are combined, driving member 3 and driving member 6 are braked, and realize one grade " 1st ".
When clutch C1 and brake B3 are combined, driving member 6 and 1 integral-rotation of input link as input shaft, Driving member 5 is braked, and realizes two grade " 2nds " less than one grade of " 1st " gearratio.
When clutch C1 and brake B2 are combined, driving member 6 and 1 integral-rotation of input link as input shaft, Driving member 4 is braked, and realizes the third gear " 3rd " less than two grades of " 2nd " gearratios.
When clutch C1 and brake B1 are combined, driving member 6 and 1 integral-rotation of input link as input shaft, Driving member 3 is braked, and realizes the fourth gear " 4th " less than third gear " 3rd " gearratio.
When clutch C1 and clutch C2 are combined, driving member 5 and driving member 6 and meanwhile with the input as input shaft 1 integral-rotation of component, realizes five grade " 5th " less than fourth gear " 4th " gearratio.
When clutch C2 and brake B1 are combined, driving member 5 and 1 integral-rotation of input link as input shaft, Driving member 3 is braked, and realizes six grade " 6ths " less than five grades of " 5th " gearratios.
When clutch C2 and brake B2 are combined, driving member 5 and 1 integral-rotation of input link as input shaft, Driving member 4 is braked, and realizes seven grade " 7ths " less than six grades of " 6th " gearratios.
When brake B1 and brake B3 are combined, driving member 3 and driving member 5 are braked, and realize reverse gear " Rev ".
Each shelves gearratio is determined by the k value of three planet rows.For example, during k1=k2 ≈ 1.712 and k3 ≈ 2.51, you can To each shelves gearratio shown in table 1, it is substantially suitable to compare between adjacent gear positions gearratio, meanwhile, the resultant gear ratio scope of drive shift (5.642/0.631) 8.941 are reached, thus obtains overall performance preferably ratio characteristic.
Three planet row PGS1～PGS3 of seven gear planetary automatic transmissions that the present invention is provided are the simple planet of single star Row, and k value is in the range of 1.7～2.6, and the radial dimension of three planet row PGS1～PGS3 can be made less, meanwhile, obtain whole Body performance preferably ratio characteristic.
The above is only the preferred embodiment of the present invention, it is noted that for the ordinary skill people of the art For member, on the premise of without departing from the technology of the present invention principle, some improvement and deformation can also be carried out, these improve and deform Also protection scope of the present invention should be regarded as.

Claims (2)

1. a kind of seven gear planetary automatic transmission, including planet row, defeated with what input shaft, output shaft were connected respectively installed in two ends Enter component (1), output link (2), driving member, brake and clutch, it is characterised in that：The planet row has three, point Wei not planet row PGS1, planet row PGS2 and planet row PGS3；The driving member has four, respectively the first driving member (3), the second driving member (4), the 3rd driving member (5) and the 4th driving member (6)；The brake has four, respectively Brake B1, brake B2, brake B3 and brake B4；The clutch has two, respectively clutch C1 and clutch C2；
The planet row PGS1 is connected with input link (1), the second driving member (4) and the first driving member (3) respectively；
The planet row PGS2 is connected with the second driving member (4), the 3rd driving member (5) and output link (2) respectively；
The planet row PGS3 is connected with the 4th driving member (6), output link (2) and the 3rd driving member (5) respectively；
The outer hub of input link (1) sun gear S1, the interior hub of clutch C1 and clutch C2 respectively with planet row PGS1 Connection；
Output link (2) are connected with the planet carrier CA3 of the gear ring R2 and planet row PGS3 of planet row PGS2 respectively；
First driving member (3) are connected with the interior hub of the gear ring R1 and brake B1 of planet row PGS1 respectively；
Second driving member (4) planet carrier CA1, sun gear S2 of planet row PGS2 respectively with planet row PGS1 and braking The interior hub connection of device B2；
3rd driving member (5) planet carrier CA2 respectively with planet row PGS2, the gear ring R3 of planet row PGS3, clutch The interior hub connection of the interior hub of C2 and brake B3；
4th driving member (6) sun gear S3 respectively with planet row PGS3, the outer hub of clutch C1 and brake B4's Interior hub connection；
The brake B1 is used for braking the first driving member (3)；
The brake B2 is used for braking the second driving member (4)；
The brake B3 is used for braking the 3rd driving member (5)；
The brake B4 is used for braking the 4th driving member (6)；
Clutch C1 connection input link (1) and the 4th driving member (6)；
Clutch C2 connection input link (1) and the 3rd driving member (5)；
The relation of ratio k1, k2, k3 of the gear ring number of teeth and the sun gear number of teeth of planet row PGS1, planet row PGS2 and planet row PGS3 For：K1=k2=1.712 and k3=2.51；The planet row is the simple planet row of single star.
2. seven gear planetary automatic transmission as claimed in claim 1, it is characterised in that：Each planet row includes the sun respectively Wheel, planet carrier and gear ring.
CN201310487758.8A 2013-10-17 2013-10-17 A kind of seven gear planetary automatic transmissions Active CN103527732B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201310487758.8A CN103527732B (en) 2013-10-17 2013-10-17 A kind of seven gear planetary automatic transmissions

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201310487758.8A CN103527732B (en) 2013-10-17 2013-10-17 A kind of seven gear planetary automatic transmissions

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CN103527732A CN103527732A (en) 2014-01-22
CN103527732B true CN103527732B (en) 2017-03-08

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Families Citing this family (12)

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Publication number Priority date Publication date Assignee Title
EP2921745A1 (en) * 2014-02-28 2015-09-23 Aisin Seiki Kabushiki Kaisha Automatic transmission for vehicle
CN104389960B (en) * 2014-09-23 2017-02-01 中国北方车辆研究所 Automatic seven-gear planetary transmission for tracked vehicle
DE102014223919B4 (en) 2014-11-25 2019-09-05 Bayerische Motoren Werke Aktiengesellschaft Combined multi-step transmission
CN104595436B (en) * 2015-02-13 2017-06-06 中国北方车辆研究所 A kind of seven gear planetary transmissions for automatic gear-box
KR101765613B1 (en) * 2015-10-15 2017-08-07 현대자동차 주식회사 Planetary gear train of automatic transmission for vehicles
CN106523628B (en) * 2016-12-16 2019-05-14 贵州凯星液力传动机械有限公司 A kind of eight-gear planetary automatic speed changer
CN107606080B (en) * 2017-10-13 2023-11-14 中南林业科技大学 A seven-speed electronically controlled mechanical planetary automatic transmission for automatic transmissions
CN108194585A (en) * 2017-10-18 2018-06-22 中国北方车辆研究所 One kind seven keeps off planetary automatic transmission
CN108131428A (en) * 2017-10-18 2018-06-08 中国北方车辆研究所 One kind six keeps off planetary automatic transmission
CN109538719A (en) * 2018-12-21 2019-03-29 中国北方车辆研究所 One kind seven keeps off planetary automatic transmission
CN109707807A (en) * 2019-03-05 2019-05-03 中国北方车辆研究所 Seven gear planetary automatic transmissions
CN113175506B (en) * 2021-04-20 2023-10-31 中国北方车辆研究所 Eight-gear compound planetary transmission mechanism with three degrees of freedom

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CN102913597A (en) * 2012-10-16 2013-02-06 中国北方车辆研究所 Seven-level planet automatic speed changer

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CN102913597A (en) * 2012-10-16 2013-02-06 中国北方车辆研究所 Seven-level planet automatic speed changer

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Effective date of registration: 20201113

Address after: No.8, Jiangfang Road, Changjiang Town, Rugao City, Nantong City, Jiangsu Province

Patentee after: North Tomson Transmission Technology Co.,Ltd.

Address before: 100072, Beijing, Fengtai District, No. 4 locust ridge hospital

Patentee before: CHINA NORTH VEHICLE Research Institute